EP3469281B1 - Dispositif de refroidissement à tubes rotatifs et procédé permettant de faire fonctionner un dispositif de refroidissement à tubes rotatifs - Google Patents

Dispositif de refroidissement à tubes rotatifs et procédé permettant de faire fonctionner un dispositif de refroidissement à tubes rotatifs Download PDF

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Publication number
EP3469281B1
EP3469281B1 EP17731066.1A EP17731066A EP3469281B1 EP 3469281 B1 EP3469281 B1 EP 3469281B1 EP 17731066 A EP17731066 A EP 17731066A EP 3469281 B1 EP3469281 B1 EP 3469281B1
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EP
European Patent Office
Prior art keywords
cooling
transport
cooled
features
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17731066.1A
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German (de)
English (en)
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EP3469281A1 (fr
Inventor
Mathias Trojosky
Karsten Kirchner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Allgaier Werke GmbH and Co KG
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Allgaier Werke GmbH and Co KG
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Publication of EP3469281A1 publication Critical patent/EP3469281A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F28F5/02—Rotary drums or rollers
    • C—CHEMISTRY; METALLURGY
    • C04—CEMENTS; CONCRETE; ARTIFICIAL STONE; CERAMICS; REFRACTORIES
    • C04B—LIME, MAGNESIA; SLAG; CEMENTS; COMPOSITIONS THEREOF, e.g. MORTARS, CONCRETE OR LIKE BUILDING MATERIALS; ARTIFICIAL STONE; CERAMICS; REFRACTORIES; TREATMENT OF NATURAL STONE
    • C04B7/00—Hydraulic cements
    • C04B7/36—Manufacture of hydraulic cements in general
    • C04B7/43—Heat treatment, e.g. precalcining, burning, melting; Cooling
    • C04B7/47—Cooling ; Waste heat management
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS, OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories, or equipment peculiar to rotary-drum furnaces
    • F27B7/38—Arrangements of cooling devices
    • F27B7/383—Cooling devices for the charge
    • F27B7/386—Rotary-drum cooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D15/00—Handling or treating discharged material; Supports or receiving chambers therefor
    • F27D15/02—Cooling
    • F27D15/0206—Cooling with means to convey the charge
    • F27D15/028—Cooling with means to convey the charge comprising a rotary drum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F28F13/125—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation by stirring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the present invention relates to a rotary tube cooler and a method for operating a rotary tube cooler and a method for cooling an item.
  • coolers are used to cool very hot products such as burnt pigments, slag, metal oxides and hydroxides, cement clinker, sponge iron, scale, activated carbon, Catalysts, coke, metallurgical residues, etc. are required. Without cooling the very hot products, further process control is often not possible. In many cases, the thermal energy contained in the solid should be recovered at least partially within the scope of the technologically necessary cooling.
  • hot bulk material such as the hot clinker to be cooled occurring in the cement industry, is introduced into several tubes arranged around a discharge end of a rotary kiln and is conveyed by the rotation of the kiln and thus the cooling tubes.
  • the cooling tubes carrying the hot product are cooled by free convection of the ambient air.
  • rotary tube coolers indirectly cooled with water, a rotary tube is sprayed with water from the outside or the drum runs through a water bath, as described in the patent U.S. 4,557,804 described, whereby the surface of the rotating drum is wetted with water and cools the apparatus wall, while in turn the hot product located in the drum is cooled by heat dissipation to the cooled apparatus wall.
  • a rotary tube cooler with a rotary tube which rotates within a fixed, brick-built envelope and in which the cooling medium (air or water) flows in the cavity formed between the rotary tube and the brickwork.
  • sectional coolers Another design that is supplied in particular by neamebach and GEA Barr-Rosin are so-called “sectional coolers”.
  • sectional coolers To increase the heat exchanger surface, e.g. 6 or 8 chambers (“sections”) created, which are located in a rotating drum housing, creating a cavity between the chambers.
  • a sectional cooler is also in document EP 2 889 569 A1 shown.
  • the goods to be cooled are transported in polygon-shaped chambers inside a drum.
  • Each chamber is designed to transport the goods to be cooled from the inlet end to the outlet end of the drum.
  • each chamber extends essentially along the entire length of the drum.
  • cooling water is passed through the cavities formed in the drum housing between the sections.
  • the cooling water is supplied and discharged via a sealed swivel joint on the product discharge side of the drum and pipe connections to and from the individual double pipes.
  • Such sectional coolers have a special design, which lead to a high material and labor cost in production, especially due to the extensive welding work required.
  • the drum case itself also necessarily has a high weight, because the drum and the walls of the chambers must be made thick-walled for reasons of strength. Both lead to a high overall weight of the apparatus.
  • sectional coolers guide the cooling water in the lower sections, as only these are flowed through with water due to gravity. A complete It is not possible to fill the sections with cooling water. As a result, the walls of the chambers ("sections") located at the top during a rotation and the hot solids located therein are not constantly and therefore not optimally cooled.
  • the flow of the cooling water in the cavities formed by the sections is not uniform, as a result of which an uneven heat transfer develops between the hot walls of the sections and the cooling water.
  • the invention is therefore based on the object of providing a device and a method with the aid of which the disadvantages of the prior art, in particular the sectional cooler, are overcome.
  • the rotary tube cooler according to the invention consists of a large number of transport pipes for transporting goods to be cooled, the large number of transport pipes being arranged around an axis of rotation and being collectively filled with goods to be cooled via a filling area, with each transport pipe being arranged essentially concentrically in a cooling pipe in which a cooling medium flows and cools the goods to be cooled via the wall of the transport pipe.
  • the large number of transport tubes are advantageously arranged in bundles in areas, these areas being suitable for mounting and / or rotating the rotary tube cooler. These areas can be designed as ring-shaped sleeves which have recesses for receiving the cooling tubes.
  • the rotation of the rotary tube cooler can advantageously take place via a toothed ring with a chain drive or a pinion. It is also possible to rotate the rotary tube cooler according to the invention via other drive variants.
  • this can be done via a friction wheel drive with driven rollers on which the raceway rests. It is also possible to set the rotary tube cooler according to the invention in rotation via a direct drive, for example via a slip-on geared motor.
  • the large number of transport pipes advantageously open into an area in which the goods to be cooled emerge, so that in this product discharge area the goods to be cooled are at a lower temperature.
  • This product discharge area is expediently essentially closed off in order to avoid dust and has further transport devices.
  • the transport tubes preferably have an inclination between 1 degree and 8 degrees, particularly preferably between 2 degrees and 5 degrees.
  • the plurality of cooling tubes are advantageously connected to one another via pipelines and also enable the cooling tubes to be acted upon by the cooling medium under pressure. This is because the possibility of being able to apply pressure to the cooling tubes means that the cooling medium can become hotter than 100 ° C. before the cooling medium begins to evaporate. In addition to water, other cooling media are also conceivable.
  • the cooling medium can reach temperatures of up to 160 ° C.
  • the cooling tubes can be pressurized.
  • the construction of the rotary tube cooler according to the invention allows both the transport and cooling tubes to be made from commercially available tubes. This eliminates the need for complex welding work that is necessary in the manufacture of the known rotary tube cooler. In addition, the use of commercially available tubes makes it easier to produce coolers that can be pressurized.
  • the direction of flow of the cooling medium runs either counter to or with the direction of transport of the item to be cooled. It must be taken into account here that the direction of transport of the goods to be cooled is predetermined by the inclination of the transport pipes. According to the invention, however, the direction of flow of the cooling medium, for example the cooling water, can be changed. It should be noted that the value of the temperature difference ⁇ between the item to be cooled and the cooling medium, for example cooling water, should always be as large as possible. Because the cooling performance is optimized by the greatest possible temperature difference ⁇ .
  • the direction of flow of the cooling medium is opposite to the direction of transport of the goods to be cooled.
  • both have the same transport direction.
  • the direction of flow of the cooling medium can also run at an angle of up to 90 ° in what is known as a cross-countercurrent or cross-cocurrent.
  • elements are provided within the transport tubes that promote mixing and circulation and the transport of the goods to be cooled.
  • Mixing and circulating the goods to be cooled has the advantage that fresh goods to be cooled are always brought into contact with the wall of the transport tube and so the temperature difference ⁇ between the wall of the Transport tube and the outer wall of the transport tube, which is surrounded by the cooling medium, is as large as possible. Because the actual indirect cooling of the goods to be cooled takes place via the transport pipe, around which the cooling medium flows.
  • Constant mixing and circulation of the goods to be cooled in the transport tube ensures that the temperature distribution within a section in the transport tube is as homogeneous as possible.
  • each transport tube can be advantageous if additional ribs and baffles are arranged in the interior of each transport tube, which increase the inner surface of the transport tube and thus favorably influence the heat transfer and mixing.
  • These elements are advantageously arranged essentially in the longitudinal direction of the transport tubes. It is also possible, however, to design these elements in the form of ribs and guide plates for generating turbulence, mixing, circulation and transport of the goods to be cooled in the form of one or more structures. These structures can be fixed or removable. These can be designed as exchangeable inserts and consist of a kind of basket that is pushed into the transport tube. It is particularly advantageous that these inserts are inexpensive to manufacture, can be easily removed from the transport tube for cleaning and maintenance purposes, and their shape and function can be adapted to the nature of the goods to be cooled. In the case of bulk goods with smaller particles, it can be advantageous to use only one basket insert which is equipped with a large number of baffles and mixing aids.
  • basket insert In the case of bulk material with larger particles, it can be advantageous to use a basket insert that has a smaller number of baffles and mixing aids. It is also possible to use a large number of basket inserts to optimize mixing according to the cooling capacity. So it can It may be expedient to induce a coarser, ie poorer, mixing at the beginning of the cooling, which becomes better in the course of the cooling, ie during the transport to the product discharge. Thanks to basket inserts with different shapes and guide plates, it is possible to adapt to the desired cooling, mixing and circulation behavior.
  • the annular gap between the transport pipe and the cooling pipe has elements which promote a turbulent flow of the cooling medium.
  • a turbulent flow in the annular gap is advantageous because it distributes the temperature distribution in the cooling medium more evenly than with a laminar flow.
  • At least one flow direction element is advantageously provided in the annular gap between the transport pipe and the cooling pipe.
  • the flow direction element according to the invention is expediently arranged on the outer wall of the transport pipe and can have different shapes. These shapes can be designed, for example, as a baffle surface or as a guide surface, or a mixed form of these two types of elements. Furthermore, it is possible that, in addition to the flat elements for deflecting the flow, there are also isolated flow direction elements which are essentially formed at points and thus generate a turbulent flow.
  • the at least one flow direction element is arranged in the form of a screw thread on the outer wall of a transport pipe.
  • This flow direction element according to the invention can be formed by applying a guide plate to the outer wall of the transport pipe, for example by welding. After completion of this flow direction element, the transport tube is pushed into the cooling tube, whereby the flow direction element does not have to come to rest on the inside of the cooling tube.
  • a second flow direction element is arranged on the outer wall of the transport pipe.
  • the second flow direction element can expediently be arranged so that it is offset by 180 ° on the outer wall and also has the shape of a screw turn.
  • flow direction elements of this type are attached to the outer wall of the transport pipe.
  • the flow direction elements are detachably connected to the transport pipe in order to be able to either service them more easily or to be able to optimally adjust the turbulent flow through certain baffles of the guide surfaces.
  • the inventive design of the cooling medium duct in the rotary tube cooler according to the invention leads to a complete flushing of the entire available heat transfer surface as well as a directed flow of the cooling medium and thus to an improvement in the cooling performance compared to known cooler designs.
  • Another embodiment of the present rotary tube cooler has a product-carrying tube instead of the tubes lying one inside the other consisting of cooling and transport tubes Tube and an enveloping sheet metal welded onto its outside, for example by spot welding.
  • the enveloping sheet metal is inflated with high pressure to produce a volume carrying the cooling medium.
  • the cooling medium is passed through the cavity that is created.
  • Double-walled heat exchanger tubes produced in this way and available in practice as standard purchased parts can further reduce the weight of the rotary tube cooler according to the invention.
  • the cooling tubes are equipped with compensators that compensate for thermal stresses. Thermal stresses can occur throughout the device due to the large temperature differences between the transport and cooling tubes. If, for example, a bulk material is filled into the filling cone at approx. 1,000 ° C, the inside of the transport pipe will heat up very quickly to this initial temperature. The temperature profile between the bulk material and the outer wall of the cooling pipe leads to a very rapid drop in temperature across the cross section, especially at the beginning of the cooling process in the vicinity of the filling cone. from the bulk material via the transport pipe, the cooling medium and finally into the outer wall of the cooling pipe. Due to the design, the transport pipe and the cooling pipe are in close proximity to one another in the filling area and are connected to one another via structural elements.
  • the cooling process is already started in the area of the product introduction.
  • the cone for the introduction of the hot solid to be cooled is double-walled and optionally integrated into the cooling medium circuit. This means that the first cooling effects can be realized very early in the process.
  • the method according to the invention uses a rotary tube cooler according to the present description and figures.
  • the method according to the invention advantageously includes the further method step, according to which the cooling medium is caused to turbulence by baffles in the annular gap between the transport tube and the cooling tube.
  • Figure 1 shows a schematic view with partial sections of a rotary tube cooler 1 according to the invention.
  • the goods to be cooled (without reference symbols) are poured into the product inlet 4 a of the filling cone 4.
  • the goods to be cooled can be transported in different ways. After the entry into the product entry 4a, the goods to be cooled fall down in the direction of arrow P1 due to gravity.
  • the tube bundles of the transport tubes 2, which are essentially concentrically enclosed by the cooling tubes 5, are located downstream of the product entry.
  • the number of transport tubes 2 can be between 3 and 9, there being basically no upper limit.
  • the key to the number of transport and cooling pipes is the controllability of the masses and ensuring the uniform rotation of the pipe bundle.
  • the transport tubes 2 are arranged together with the cooling tubes 5 around a rotation axis 3 and rotate, driven by a toothed ring or chain drive 9 over the bearing 7.
  • a toothed ring or chain drive 9 over the bearing 7.
  • bearings these as races 6, 8 are formed.
  • the position of the races 6, 8 is determined by the dimensions of the rotary tube cooler according to the invention. A larger number of bearings can be useful with other dimensions.
  • the goods to be cooled are transported along the arrows P2 and P3 into the transport tubes 2 below (in the present sectional view this is only a transport tube 2) and, due to the inclination of the transport tubes, moves between 1 ° and 9 ° along the arrows shown P3 and P4 in Figure 1 to the left.
  • Elements are provided in the transport tubes (not in Figure 1 shown), which promote and promote the transport, circulation, shifting and mixing of the goods to be cooled.
  • the transport pipes 2 are surrounded by an annular gap which is delimited by the cooling pipes 5 (see in detail in the following figures).
  • the cooling medium for example water, flows through this annular gap.
  • the cooling medium is introduced into the cooling tubes 5 via a circuit 11, 11a, 11b, 11c and 11d and discharged.
  • the cooling medium flows through the inlet 11 in the direction of arrow K1 at a first temperature, for example approx. 10 ° C, into the cooling circuit and from there via spoke-like feed lines 11b into the cooling tubes 5.
  • the cooling medium is transported in countercurrent to the cooling of the goods to be cooled .
  • the cooling medium flows through spoke-like discharge lines 11c in the direction of the arrow K3 into a central drainage pipe 11d and leaves the cooling circuit there in the direction of the arrow K4.
  • the material to be cooled is conveyed in the transport pipes 2 to the product discharge 10 and there leaves the rotary tube cooler according to the invention in the direction of arrow P5, preferably due to gravity.
  • FIG 2 shows a schematic sectional view through the tube bundle of the rotary tube cooler according to the invention with, as selected in this embodiment, six cooling tubes 5 and six transport tubes 2.
  • the cooling medium is fed into the cooling circuit through the tube 11a. From there, the cooling medium flows via the supply pipes 11b into the cooling pipes 5.
  • the supply pipes 11b are arranged like spokes and, due to their fully round cross-section, are suitable for being pressurized.
  • the inlet pipes 11b cover in Figure 2 the discharge pipes 11c, which are also arranged like spokes and through which the cooling medium flows back, in order to finally leave the cooling circuit again via the line 11d.
  • the transport tubes 2 In each of the cooling tubes 5, separated by an annular gap, the transport tubes 2, in which the goods to be cooled are transported, are arranged.
  • FIG 3 shows an enlarged sectional view through a cooling pipe 5 and a transport pipe 2, the proportions of the dimensions not corresponding to reality.
  • the annular gap A through which the cooling medium flows must be dimensioned so that both the heat exchange and the removal of the cooling medium are optimized. To this end, it is advantageous that a flow that is as turbulent as possible is built up in the annular gap.
  • the wall thickness of the transport tube 2 should be dimensioned so that the heat exchange can take place as quickly as possible. The thinner the wall thickness, the faster the heat is dissipated from the goods to be cooled. However, a thin wall thickness is at the expense of the stability of the transport tube 2. It is important to find an optimal dimensioning for this.
  • the wall thickness of the cooling tube 5 is relevant both for the stability and for the heat exchange with the environment.
  • Figure 4 shows a schematic longitudinal section through a transport tube 2 and a cooling tube 5.
  • the annular gap A is not to scale, and the wall thicknesses of the cooling tube 5 and the transport tube 2 are not to scale.
  • Elements 12 are arranged in the transport tube 2 which promote and promote mixing, circulation and transport in the direction of P3.
  • the arrangement of the cooling pipes 5 and transport pipes 2 according to the invention is expediently relative to the horizontal inclined, preferably between 1 degree and 8 degrees, particularly preferably between 2 degrees and 5 degrees. This inclination and the use of the elements 12 facilitate transport through the transport tube 2.
  • the cooling medium flows in the direction of K2, ie in countercurrent operation.
  • Figure 5 shows a schematic cross section through the arrangement according to the invention according to claim 4, wherein the elements 12 are not to scale.
  • the shape of the elements is also only shown schematically.
  • An element 12 can be designed as a straight baffle plate, it can also have a curvature or perforations or consist of agitator-like ends which serve to bring about a good mixing of the material to be cooled for the uniform temperature distribution. It is also possible for elements in different temperature zones of the transport tube 2 to have different shapes.
  • FIG. 6 shows a schematic longitudinal section through a cooling pipe 5 and flow direction element 14, which is applied to the outer wall of the transport pipe 2 and thus lies completely in the annular gap A.
  • the flow direction element 14 can be in one piece, as shown, or in several pieces.
  • the flow direction element 14 shown runs around the outer wall of the transport tube 2 in the manner of a screw turn and forces the cooling medium onto a turbulent flow path in the direction of the arrow K2 '.
  • the flow direction K2 ' also has the advantage that the distance covered by any cooling medium particle is significantly longer than the length of the cooling pipe 2. This also has a favorable effect on the heat transfer, since the cooling medium can absorb heat longer than if it were only along the length the cooling pipe rafts. To further improve the turbulence in the cooling medium, which is responsible for a thorough mixing of the cooling medium, it can be useful to break through the webs of the flow direction element 14 at some points.
  • Figure 7 shows a section through a cooling pipe 5 with compensators 15 which are arranged at one end of the cooling pipe 5.
  • the compensator 15 consists of a plurality of bellows-shaped turns. Due to high temperature differences between the cooling tube and the cooling medium, stresses can occur in the cooling tube 5. These stresses, which can run in both the longitudinal and transverse directions of the cooling tube, are absorbed and reduced by the compensator 15, since the compensator 15 is structurally capable of yielding such stresses through defined deformation.
  • Figure 8 shows a schematic temperature diagram over the course of the temperature from the center of the transport pipe 2 to the ambient temperature outside the cooling pipe 5. Assuming that the goods to be cooled are poured into the filling cone at a temperature of A ° C, the goods to be cooled will when entering a transport tube, the core should already cool slightly and the temperature steadily decrease towards the outside. As soon as the material to be cooled touches the inner wall of the transport tube 2, a significant cooling effect will be observed, which is indicated in FIG. 8 by the temperature B ° C. The temperature profile in the pipe wall of the transport pipe 2 will be essentially linear. A temperature of C ° C. would therefore be applied to the outer wall of the transport tube 2.
  • the cooling medium In the annular gap of the cooling pipe 5 and the transport pipe 2, the cooling medium ideally flows in a turbulent flow, although a temperature profile can be determined which runs from a higher temperature C ° C to a lower temperature D ° C. Finally, a temperature profile from D ° C to E ° C can be determined in the cooling tube wall. Outside the cooling tube 5, the ambient temperature is present.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Materials Engineering (AREA)
  • Structural Engineering (AREA)
  • Organic Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Muffle Furnaces And Rotary Kilns (AREA)
  • Heat Treatment Of Articles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (18)

  1. Refroidisseur à tubes rotatifs (1) composé d'une pluralité de tubes de transport (2) pour le transport d'une matière à refroidir indirectement, dans lequel la pluralité de tubes de transport (2) sont disposés autour d'un axe de rotation (3) et peuvent être remplis ensemble de la matière à refroidir par une zone de remplissage (4), caractérisé en ce que chaque tube de transport (2) est disposé de manière concentrique dans un tube de refroidissement (5) et le refroidissement indirect de la matière à refroidir a lieu par le tube de transport autour duquel circule le milieu de refroidissement et qui refroidit la matière à refroidir par l'intermédiaire de la paroi du tube de transport (2).
  2. Refroidisseur à tubes rotatifs (1) selon la revendication 1, caractérisé en ce que la pluralité de tubes de transport (2) sont disposés en faisceau dans des zones (6, 7, 8) et ces zones (6, 7, 8) sont appropriées au montage ou à la rotation du refroidisseur à tubes rotatifs (1).
  3. Refroidisseur à tubes rotatifs (1) selon la revendication 2, caractérisé en ce que la rotation s'effectue par l'intermédiaire d'une couronne dentée à entraînement par chaîne (9) ou d'un pignon.
  4. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que la pluralité de tubes de transport (2) débouchent dans une zone dans laquelle la matière à refroidir sort.
  5. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que les tubes de transport (2) sont inclinés de la zone de l'entrée de produit (4, 4a) à la zone de la sortie de produit (10).
  6. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que la pluralité de tubes de refroidissement (5) sont reliés entre eux par des conduites.
  7. Refroidisseur à tubes rotatifs (1) selon la revendication 6, caractérisé en ce que les tubes de refroidissement (5) peuvent être mis sous pression.
  8. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que le sens d'écoulement du milieu de refroidissement va au choix à l'encontre ou dans le sens de transport de la matière à refroidir.
  9. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que des éléments (12) sont prévus à l'intérieur des tubes de transport (2), lesquels favorisent le mélange et la circulation de la matière à refroidir.
  10. Refroidisseur à tubes rotatifs (1) selon la revendication 9, caractérisé en ce que les éléments (12) sont disposés sensiblement dans la direction longitudinale des tubes de transport (2).
  11. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que l'espace annulaire (A) entre le tube de transport (2) et le tube de refroidissement (2) comprend des éléments (12) qui favorisent un écoulement turbulent du milieu de refroidissement.
  12. Refroidisseur à tubes rotatifs (1) selon l'une des revendications 1 à 10, caractérisé en ce qu'au moins un élément directeur d'écoulement (14) est prévu dans l'espace annulaire entre le tube de transport et le tube de refroidissement.
  13. Refroidisseur à tubes rotatifs (1) selon la revendication 12, caractérisé en ce que ledit au moins un élément directeur d'écoulement (14) est disposé sur la paroi extérieure d'un tube de transport (2).
  14. Refroidisseur à tubes rotatifs (1) selon la revendication 13, caractérisé en ce que ledit au moins un élément directeur d'écoulement (14) est disposé sous la forme d'une hélice sur la paroi extérieure d'un tube de transport (2).
  15. Refroidisseur à tubes rotatifs (1) selon l'une des revendications précédentes, caractérisé en ce que les tubes de refroidissement (5) sont équipés de compensateurs (15) qui compensent les contraintes thermiques.
  16. Procédé de refroidissement d'une matière en vrac au moyen d'un refroidisseur à tubes rotatifs selon l'une des revendications 1 à 15.
  17. Procédé de refroidissement d'une matière en vrac selon la revendication 16, comprenant les étapes consistant à :
    1. introduire une matière à refroidir dans un tube de transport qui est entouré par un tube de refroidissement dans lequel s'écoule un milieu de refroidissement, le milieu de refroidissement étant de l'eau ;
    2. transporter la matière à refroidir d'une extrémité du tube de transport à son autre extrémité, la matière à refroidir étant refroidie en continu par le milieu de refroidissement;
    3. faire tourner en continu les tubes de transport autour d'un axe ;
    4. faire sortir la matière de transport refroidie.
  18. Procédé de refroidissement d'une matière en vrac selon la revendication 17, comprenant en outre l'étape selon laquelle le milieu de refroidissement est mis en turbulence par des chicanes dans l'espace annulaire entre le tube de transport et le tube de refroidissement.
EP17731066.1A 2016-06-14 2017-06-12 Dispositif de refroidissement à tubes rotatifs et procédé permettant de faire fonctionner un dispositif de refroidissement à tubes rotatifs Active EP3469281B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016007221.0A DE102016007221B4 (de) 2016-06-14 2016-06-14 Drehrohrkühler und Verfahren zum Betreiben eines Drehrohrkühlers
PCT/EP2017/000687 WO2017215784A1 (fr) 2016-06-14 2017-06-12 Dispositif de refroidissement à tubes rotatifs et procédé permettant de faire fonctionner un dispositif de refroidissement à tubes rotatifs

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EP3469281A1 EP3469281A1 (fr) 2019-04-17
EP3469281B1 true EP3469281B1 (fr) 2020-08-26

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US (1) US11530881B2 (fr)
EP (1) EP3469281B1 (fr)
CA (1) CA3026581C (fr)
DE (1) DE102016007221B4 (fr)
ES (1) ES2830399T3 (fr)
MA (1) MA45230B1 (fr)
WO (1) WO2017215784A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016007221B4 (de) * 2016-06-14 2018-10-25 Allgaier Werke Gmbh Drehrohrkühler und Verfahren zum Betreiben eines Drehrohrkühlers
JP7169923B2 (ja) * 2019-03-27 2022-11-11 日本碍子株式会社 熱交換器
FI128481B (en) 2019-06-11 2020-06-15 Kopar Oy Rotary condenser and method for performing cooling and transport simultaneously
KR102390012B1 (ko) * 2020-06-09 2022-04-28 제일산기 주식회사 고온 브리켓 철의 냉각장치
CN113606816B (zh) * 2021-09-07 2022-11-18 哈尔滨商业大学 一种用于制冷设备的热交换装置
CN114562900B (zh) * 2022-03-10 2023-08-18 江苏经贸职业技术学院 一种直接蒸发旋转式表冷器装置
EP4325152A1 (fr) * 2022-08-19 2024-02-21 Alite GmbH Refroidisseur d'argile calcinée

Family Cites Families (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1218873A (en) 1913-11-29 1917-03-13 William Lennon Trough or flume.
US1711297A (en) 1928-02-06 1929-04-30 Wiltse Appliance Co Pump mechanism
US2137373A (en) * 1936-09-29 1938-11-22 Vogt & Co Inc Henry Double pipe chiller
US2283129A (en) 1940-11-25 1942-05-12 Allis Chalmers Mfg Co Rotary clinker cooler
DE830471C (de) * 1941-07-03 1952-02-04 Fuller Co Verfahren und Vorrichtung zum Kuehlen von Zement
US2362539A (en) 1942-07-21 1944-11-14 Traylor Engineering And Mfg Co Rotary water-cooled tube cooler
US2348446A (en) 1943-08-09 1944-05-09 Allis Chalmers Mfg Co Rotary cooler
FR995986A (fr) * 1945-04-03 1951-12-11 Perfectionnements apportés aux échangeurs de chaleur notaminent à ceux servant àla pasteurisation du lait
US2971751A (en) * 1958-02-11 1961-02-14 Smidth & Co As F L Cooling apparatus
NL271716A (fr) * 1960-11-23
FR1331071A (fr) * 1961-08-17 1963-06-28 Bayer Ag Dispositif de traitement continu des liquides
US3208512A (en) * 1963-07-24 1965-09-28 Dravo Corp Heat exchanger for rotary kiln and the like
US3604125A (en) * 1969-11-19 1971-09-14 Allis Chalmers Mfg Co Tubular rotary cooler
NO122742B (fr) * 1970-05-16 1971-08-02 Stord Bartz Industri As
US3667542A (en) * 1971-01-05 1972-06-06 Ralph C Parkes Heat transfer roll
US3788392A (en) * 1971-07-06 1974-01-29 Fmc Corp Revolving linear tube heat exchanger
BE792880A (fr) 1971-12-15 1973-03-30 Kloeckner Humboldt Deutz Ag Refroidisseur a satellites pour four tubulaire rotatif
US3845941A (en) * 1972-09-05 1974-11-05 Robert Lamar Mendenhall Apparatus for producing asphalt-aggregate compositions
ZA74222B (en) 1973-02-01 1975-01-29 Polysius Ag Planetary cooler
DE2424224B2 (de) * 1974-05-17 1976-03-18 Polysius Ag, 4723 Neubeckum Drehrohrofen mit satellitenkuehler
GB1447349A (en) 1975-03-18 1976-08-25 Smidth & Co As F L Planetary coolers
GB1502351A (en) 1975-07-23 1978-03-01 Smidth & Co As F L Planetary cooler
US4131418A (en) 1977-05-23 1978-12-26 Fuller Company Tube coolers for rotary kilns
DE2936199A1 (de) * 1979-09-07 1981-03-19 Didier Engineering Gmbh, 4300 Essen Verfahren bzw. vorrichtung zur ueberhitzung gasfoermiger medien
FR2495301A1 (fr) * 1980-11-28 1982-06-04 Euro Machines Dispositif pour le chauffage ou le refroidissement de produits visqueux
US4377202A (en) * 1981-05-26 1983-03-22 Fuji Kosan Kabushiki Kaisha Rotary heat exchange apparatus provided with a spherically coiled heat transfer tube
DK381783A (da) * 1982-09-02 1984-03-03 Kawasaki Heavy Ind Ltd Calcineringsapparat med planetkoeler
FI71837C (fi) 1982-11-26 1987-02-09 Partek Ab Nedloppskonstruktion foer kylare i roterugn.
DD214194A1 (de) * 1983-03-31 1984-10-03 Dessau Zementanlagenbau Veb Verfahren und vorrichtung zur rueckgewinnung von wandwaerme
US4557804A (en) 1984-05-18 1985-12-10 Triten Corporation Coke cooler
SE458431B (sv) 1985-03-27 1989-04-03 Max Segerljung Anordning foer att maskinellt klyva klyvningsbara foeremaal
DE3534991A1 (de) 1985-10-01 1987-04-02 Gutehoffnungshuette Man Drehrohrkuehler
US4640344A (en) * 1986-03-04 1987-02-03 Manco Corporation Self-cleaning, rotary heat exchanger
DE3722319A1 (de) * 1987-07-07 1989-01-19 Bayer Ag Waermetauscher
AT398129B (de) 1991-01-14 1994-09-26 Waagner Biro Ag Drehrohrwärmebehandlungsanlage, insbesondere drehrohrofen
DE4406382C2 (de) 1994-02-26 1997-08-14 Metallgesellschaft Ag Drehkühler zum Kühlen von Schüttgut
FR2818367A1 (fr) * 2000-12-15 2002-06-21 Db Ind Appareil a enveloppes tubulaires coaxiales tel qu'un echangeur de temperature annulaire
DE10230511C1 (de) * 2002-07-06 2003-08-14 Alfred Liebig Gasabdichtungseinheit für Hoch- und Schachtöfen
EP2889569A1 (fr) * 2013-12-26 2015-07-01 Technip France Refroidisseur rotatif comprenant un système d'air de balayage contrôlé
DE102016007221B4 (de) * 2016-06-14 2018-10-25 Allgaier Werke Gmbh Drehrohrkühler und Verfahren zum Betreiben eines Drehrohrkühlers

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2017215784A1 (fr) 2017-12-21
CA3026581A1 (fr) 2017-12-21
DE102016007221B4 (de) 2018-10-25
US11530881B2 (en) 2022-12-20
EP3469281A1 (fr) 2019-04-17
DE102016007221A1 (de) 2017-12-14
US20190186835A1 (en) 2019-06-20
CA3026581C (fr) 2024-01-09
ES2830399T3 (es) 2021-06-03
MA45230B1 (fr) 2020-10-28

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